CN105814290B - Exhaust valve actuator and internal combustion engine with the exhaust valve actuator - Google Patents
Exhaust valve actuator and internal combustion engine with the exhaust valve actuator Download PDFInfo
- Publication number
- CN105814290B CN105814290B CN201480062833.9A CN201480062833A CN105814290B CN 105814290 B CN105814290 B CN 105814290B CN 201480062833 A CN201480062833 A CN 201480062833A CN 105814290 B CN105814290 B CN 105814290B
- Authority
- CN
- China
- Prior art keywords
- cylinder
- piston
- air bleeding
- valve
- recess portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
Abstract
The present invention provides a kind of exhaust valve actuator, can utilize the close moment for changing air bleeding valve suitable for the simple structure of marine engine, make the characteristic adaptation operational situation of internal combustion engine.Exhaust valve actuator (1) has：Piston (7) is arranged on the air bleeding valve (5) of internal combustion engine；Cylinder (9) accommodates piston (7)；Hydraulic pressure supplying device (13), from cam (35) drive and at the defined valve opening moment intermittently to cylinder (9) for oil feed pressure, and push piston (7) make air bleeding valve (5) open；Air spring assembly (15) exerts a force to air bleeding valve (5) to valve closing direction；Protrusion (7a) is formed on the top surface of piston (7) and has the topside area smaller than the cross-sectional area of piston (7)；Recess portion (9a), is formed in the inside top surface of cylinder (9), and when piston (7) rise, protrusion (7a), which is separated with, to be inserted into gap in recess portion (9a)；Actuator (17) changes the depth of recess portion (9a)；And control device (19), control actuator (17).
Description
Technical field
Make the exhaust valve actuator of dynamic formula the present invention relates to a kind of oil pressure and in the exhaust valve actuator
Combustion engine, the exhaust valve actuator utilize the oil pressure of the start oil sprayed from the jumper bar being cam-driven to push setting and are being vented
The piston of valve shaft end is to open air bleeding valve.
Background technology
This exhaust valve actuator can be controlled by operating oil pressure, make exhaust according to the operating load of internal combustion engine
The switching time of valve keeps best.
For example, in Modeling of Large Two-Stroke Marine Diesel Engine, pass through the closing in high loaded process time delay heel row air valve
Moment can prevent the compression pressure of gas in cylinder excessively high and improve the durability of internal combustion engine.Further, it is possible to make exhaust valve closure
Speed reduce and so that air bleeding valve is not hit valve seating, damage, abrasion etc. to inhibit air bleeding valve and valve seating.
However, in the general mechanical exhaust valve actuator for directly driving air bleeding valve by cam, due to air bleeding valve
Profile of the action depending on cam, therefore when changing the switching time of air bleeding valve, need that different multiple convex of profile is arranged
Wheel or the therebetween complicated structure such as variable rocking arm of setting leverage.Therefore it is not particularly suited for wanting to avoid the ship of marine failure
With the exhaust valve actuator of internal combustion engine.
In patent document 1, it discloses and a kind of as described above delayed the oil pressure at exhaust valve closure moment and make dynamic formula row
Air valve driving device.As shown in the Fig.1 of same document, the shaft end in air bleeding valve 5 is set and by air bleeding valve 5 to valve opening position
The piston 10 of pushing is two sections of pistons with large diameter portion and small diameter portion, and the cylinder 4 which is slided also is with big mouth
Diameter and small-bore two sections of barrel shapes.
It is supplied from the start oil of the oil pressure pump force feed being cam-driven via oil circuit 11 small-bore to cylinder 4, passes through it
Oil pressure forces down piston 10, and air bleeding valve 5 is opened.Also, when air bleeding valve 5 is closed, until the small diameter portion of piston 10 pours cylinder 4
Air bleeding valve 5 carries out quick closedown until in small-bore, when the small diameter portion of piston 10 start to pour cylinder 4 it is small-bore when, enclose
Start oil between the small diameter portion and the large-diameter portion of cylinder 4 of piston 10 is by the gap between cylinder 4 and piston 10 to cylinder 4
Small diameter portion flows into, and flow resistance at this moment is to the mobile generation cushioning effect of piston 10, the valve closing speed reduction of air bleeding valve 5.Cause
This, air bleeding valve 5 contacts valve seating with more slow speed, from the impact caused by the collision with valve seating.
Existing technical literature
Patent document
Patent document 1：Japanese Patent Laid-Open 1-244111 bulletins
Invention content
The subject that the invention solves
However, in exhaust valve actuator described in patent document 1, degree one that 5 close moment of air bleeding valve is delayed
It is fixed, such as can not delay or further delay the close moment of air bleeding valve 5.Accordingly, it is difficult to change the characteristic of internal combustion engine with suitable
Answer various operational situations.
The present invention completes in view of the above fact, provides a kind of exhaust valve actuator and has air bleeding valve driving
The internal combustion engine of device, the exhaust valve actuator can change air bleeding valve by the simple structure suitable for marine engine
Close moment makes the characteristic adaptation operational situation of internal combustion engine.
Technical solution
To solve the above subject, exhaust valve actuator of the invention and the internal combustion engine with the exhaust valve actuator
Using following methods.
The 1st mode of the present invention is a kind of exhaust valve actuator, is had：The air bleeding valve in internal combustion engine is arranged in piston
On；Cylinder accommodates the piston；Oil pressure feed mechanism is connect via oil hydraulic circuit with the cylinder, by actuated by cams and
At the defined valve opening moment intermittently to the cylinder for oil feed pressure, and pushing the piston makes the air bleeding valve open；It closes
Valve force application mechanism exerts a force to the air bleeding valve to valve closing direction；Protrusion, be formed on the top surface of the piston and with than
The small topside area of the cross-sectional area of the piston；Recess portion is formed in the inside top surface of the cylinder, is risen in the piston
When, the protrusion, which is separated with, to be inserted into gap in the recess portion；Actuator changes the depth of the recess portion；And control machine
Structure, controls the actuator, and the cylinder has：Positioned at the columned first component of central part；And it is arranged described
Around first component and relative to the second component of the relatively-movable cylindrical shape of the first component, the first component
Lower surface is located at the top of the lower surface of the second component, the recess portion be it is the lower section of the first component, described second
The space of the inner circumferential side of component, the actuator change the depth of the recess portion by the movement second component.
The another way of the present invention is a kind of exhaust valve actuator, is had：The exhaust in internal combustion engine is arranged in piston
On valve；Cylinder accommodates the piston；Oil pressure feed mechanism is connect via oil hydraulic circuit with the cylinder, by actuated by cams
And at the defined valve opening moment intermittently to the cylinder for oil feed pressure, and pushing the piston makes the air bleeding valve open；
Valve closing force application mechanism exerts a force to the air bleeding valve to valve closing direction；Protrusion is formed on the top surface of the piston and has
The topside area smaller than the cross-sectional area of the piston；Recess portion is formed in the inside top surface of the cylinder, on the piston
When rising, the protrusion, which is separated with, to be inserted into gap in the recess portion；Actuator changes the depth of the recess portion；And control
Mechanism, controls the actuator, and the cylinder has：Positioned at the columned third component of central part, the third component
Lower surface be located at the cylinder inside top surface lower section, the recess portion is inner peripheral surface and the third component of the cylinder
Peripheral surface between space, the actuator changes the depth of the recess portion by the movement third component.
According to above structure, when oil pressure feed mechanism is cam-driven, at the defined valve opening moment to cylinder for oil supply
Thus pressure pushes the piston of cylinder interior and opens air bleeding valve.Also, when the oil pressure that is supplied to cylinder reduces, air bleeding valve by
It is closed in the force of valve closing force application mechanism.
When exhaust valve closure, enter cylinder interior with the piston that air bleeding valve integrally acts, until being formed in the top of piston
Until the recess portion being formed in the inside top surface of cylinder is inserted into protrusion on face, air bleeding valve is closed with faster speed.Then, when
When the protrusion of piston starts to pour the recess portion of cylinder, enclosed start oil between protrusion and cylinder passes through between protrusion and recess portion
Close gap is flowed out to outside cylinder, and at this moment larger flow resistance plays cushioning effect, the valve closing of air bleeding valve to the action of piston
Speed reduces.Therefore, air bleeding valve contacts valve seating with more slow speed, from the impact caused by the collision with valve seating.
The depth of the recess portion of cylinder can be changed by actuator and control mechanism.When the depth of recess portion is smaller,
The amount of enclosed start oil between protrusion and cylinder is reduced, therefore the cushioning effect of piston reduces, and air bleeding valve will be close to by convex
The more early moment at the valve closing moment of the profile defined of wheel closes.
Also, when the depth of recess portion is larger, the amount of enclosed start oil between protrusion and cylinder increases, therefore it is discharged
Will be more time-consuming, the cushioning effect of piston increases.Therefore, air bleeding valve will be delayed at the valve closing moment than the profile defined by cam
At the time of close.
So, by changing the depth being arranged in the recess portion of cylinder side, it can shift to an earlier date or delay the closing of air bleeding valve
Moment, therefore the characteristic adaptation operational situation of internal combustion engine can be made.
Also, the change at exhaust valve closure moment is due to can be with changing as the depth of recess portion being arranged on cylinder
Simple structure is completed, therefore the marine engine suitable for being desirable for simple structure.
In said structure, the control mechanism preferably structure of the actuator in order to control, to make the recess portion
Depth increases with the rising of the load of the internal combustion engine.
According to the structure, the close moment of air bleeding valve is as the load of internal combustion engine rises and delays.Thereby, it is possible to prevent height
The compression pressure of gas is excessively high and improve the durability of internal combustion engine in cylinder when load running.
The 2nd mode of the present invention is a kind of exhaust valve actuator, is had：The air bleeding valve in internal combustion engine is arranged in piston
On；Cylinder accommodates the piston；Oil pressure feed mechanism, from actuated by cams and the defined valve opening moment intermittently to
The cylinder is for oil feed pressure, and pushing the piston makes the air bleeding valve open；Valve closing force application mechanism, to the air bleeding valve to
Valve closing direction exerts a force；Leakage path releases the oil pressure generated by the oil pressure feed mechanism；Flow control device changes
The area of passage of the leakage path；And control mechanism, control the flow control device.
It is identical as the 1st mode according to above structure, when oil pressure feed mechanism is cam-driven, opened defined
Thus the valve moment pushes the piston of cylinder interior and opens air bleeding valve to cylinder for oil feed pressure.Also, it is supplied when interrupting to cylinder
When oil pressure, air bleeding valve is closed due to the force of valve closing force application mechanism.
A part for the start oily (oil pressure) supplied from oil pressure feed mechanism is from the flow-rate adjustment being arranged on leakage path
Agencies are to the outside of oil hydraulic circuit.The oil mass backflowed as a result, from cylinder to oil pressure feed mechanism when air bleeding valve valve closing is less than
By oil pressure feed mechanism, force feed is to the oil mass of cylinder under pressure, therefore when air bleeding valve valve closing, piston can return conscientiously
In air return cylinder, so as to close air bleeding valve conscientiously.
By controlling flow control device, the start oil supplied from oil pressure feed mechanism can be adjusted and leak into outside
Amount.When the leakage rate is smaller, the speed of exhaust valve closure slows down, and when leakage rate is larger, the speed of exhaust valve closure is accelerated.
So, it is flowed by being arranged on the oil pressure generated by oil pressure feed mechanism to be released to external leakage path
Regulating mechanism is measured, can shift to an earlier date or delay the close moment of air bleeding valve, therefore the characteristic adaptation operational situation of internal combustion engine can be made.
Also, the change at exhaust valve closure moment due to can in the upper setting leakage path such as oil hydraulic circuit or cylinder and
Simple structure as flow control device is completed, therefore the marine engine suitable for being desirable for simple structure.
In said structure, the control mechanism preferably structure of the flow control device in order to control, it is described to make
The area of passage of leakage path reduces with the rising of the load of the internal combustion mechanism.
According to the structure, the close moment of air bleeding valve can prevent high load capacity as the load of internal combustion engine rises and delays
The compression pressure of gas is excessively high and improve the durability of internal combustion engine in cylinder when operating.
The 3rd mode of the present invention is a kind of internal combustion engine, has exhaust valve actuator described in any one of the above embodiments.
The simple structure suitable for marine engine can either be formed as a result, and can change the close moment of air bleeding valve,
It can make the characteristic adaptation operational situation of internal combustion engine.
Advantageous effect
As described above, according to exhaust valve actuator according to the present invention and in the exhaust valve actuator
Combustion engine can utilize the close moment for changing air bleeding valve suitable for the simple structure of marine engine, thus can make internal combustion engine
Characteristic adaptation operational situation, and the reliability and durability of internal combustion engine can be improved, while additionally aiding and saving fuel etc..
Description of the drawings
Fig. 1 is the summary composition figure for indicating the exhaust valve actuator involved by first embodiment of the present invention.
Fig. 2 is the enlarged drawing of the parts II in Fig. 1, and (a) is to indicate that the state before the recess portion of cylinder is inserted into the protrusion of piston
Longitudinal section, be (b) to indicate that the protrusion of piston is initially inserted into the longitudinal section of the state of the recess portion of cylinder.
Fig. 3 is the figure of the other shapes example of the protrusion for indicating piston and the recess portion of cylinder, and (a) is to indicate that the protrusion of piston is inserted
Enter the longitudinal section of the state before the recess portion of cylinder, is (b) to indicate that the protrusion of piston is initially inserted into the state of the recess portion of cylinder
Longitudinal section.
Fig. 4 (a), (b), (c) are cam lifting amount, start oil pressure, the air bleeding valve lifting amount for indicating the 1st embodiment respectively
Chart.
Fig. 5 is the summary composition figure for indicating the exhaust valve actuator involved by second embodiment of the present invention.
Fig. 6 (a), (b), (c) are cam lifting amount, start oil pressure, the air bleeding valve lifting amount for indicating the 2nd embodiment respectively
Chart.
Specific implementation mode
Referring to the drawings, the embodiment of exhaust valve actuator according to the present invention is illustrated.
[the 1st embodiment]
Fig. 1 is the summary composition figure for indicating the exhaust valve actuator involved by first embodiment of the present invention.The air bleeding valve
Driving device 1 is arranged in marine main engine on diesel engine (internal combustion engine).
Marine main engine diesel engine (hereinafter referred to as " diesel engine ") be such as low speed two-stroke machine, using supply gas from below to
The uniflow type of the uniflow scavenging of top exhaust.The output of diesel engine via propeller shaft not shown in the figure directly or indirectly with
Propeller connects.
As shown in Figure 1, exhaust valve actuator 1 has：Air bleeding valve 5, to the row being formed in the cylinder head 3 of diesel engine
Air-flow road is switched；Piston 7 is arranged on air bleeding valve 5；Cylinder 9 accommodates piston 7；Oil hydraulic circuit 11 and oil pressure supply
Device (oil pressure feed mechanism) 13, to cylinder 9 for oil feed pressure；Air spring assembly (valve closing force application mechanism) 15, to exhaust
Valve 5 exerts a force to valve closing direction (being in Fig. 1 top)；Actuator 17 and control device (control mechanism) 19.
Piston 7 is connect with the upper end of the axle portion 5a of air bleeding valve 5 extended in the vertical direction, and opening with air bleeding valve 5
Pass moves back and forth along the vertical direction in cylinder 9.By one end of hydraulic chamber 21 and oil hydraulic circuit 11 that piston 7 and cylinder 9 are formed
11a connections.Also, extend throttling circuit 25 from the hydraulic chamber 21, in the throttling on circuit 25, being provided with as solid
Determine the throttling set 27 of throttle valve.In addition, air bleeding valve 5 is exerted a force by air spring assembly 15 to valve closing direction (top) always.
Hydraulic pressure supplying device 13 is the structure with jumper bar 31, cylinder 33 and cam 35.Jumper bar 31 is freely slidablely
It is inserted into cylinder 33, compression chamber 37 is connect with the other end 11b of oil hydraulic circuit 11, and the compression chamber 37 is by jumper bar 31 and cylinder
33 form, and the jumper bar 31 is exerted a force by force application mechanism not shown in the figure to the direction (lower section) for being detached from cylinder 33 always.
In the lower part of jumper bar 31, cam roller 41 is supported by via connecting shaft 39.Cam roller 41 is along arranged below
The peripheral surface of cam 35 rotates on cam contour.43 one of camshaft that cam 35 is rotated with the crankshaft-synchronous with diesel engine
Setting.
In oil hydraulic circuit 11, low pressure start oil supply circuit 45 is branched out from branch point 11c.It is supplied in the low pressure start oil
To on circuit 45, it is connected with low pressure start oil sources not shown in the figure via check valve 47, is supplied for opening air bleeding valve 5
As the oil pressure of benchmark when pass.When the oil pressure in oil hydraulic circuit 11 is below specified value, check valve 47 is opened, from low pressure start
It is oily (oil pressure) that oily supply circuit 45 supplements start.Also, when the pressure in oil hydraulic circuit 11 reaches specified value or more, that is, pass through
When jumper bar 31 carries out pressure process, check valve 47 is closed.
As shown in Fig. 2 (a), (b), the central portion in the top surface of piston 7 is formed with columned protrusion 7a.Protrusion 7a's
Topside area is smaller than the cross-sectional area of piston 7.For example, it is assumed that a diameter of 80 millimeters of piston 7, then can be convex shown in example
A diameter of 50 millimeters or so of portion 7a, height of the protrusion 7a apart from top surface be 60 millimeters or so, but be not limited to the size or
The diameter proportion.
In addition, the central portion in the inside top surface of cylinder 9 is formed with the poroid recess portion 9a of cylinder.The internal diameter of recess portion 9a is set
It is set to when piston 7 rises, the protrusion 7a of piston 7 is separated with several millimeters or so of gap and the size be inserted into.
The depth h of recess portion 9a can change between from zero to height identical with the height of protrusion 7a.Example
Such as, the structure at the top of cylinder 9 is the movable link 9c of cylindrical shape closely and can relatively movably be arranged in center up and down
Structure around the columned fixing component 9b in portion, the sky of the lower section of fixing component 9b, movable link 9c inner circumferential side
Between constitute recess portion 9a.In addition, oil hydraulic circuit 11 is open to the lower surface of fixing component 9b.
Also, by making movable link 9c move up and down with actuator 17 shown in FIG. 1, the depth of recess portion 9a can be changed
h.Such as, it may be considered that by the way that screw pair will be set as between the peripheral surface of fixing component 9b and the inner peripheral surface of movable link 9c, and
Movable link 9c is set to carry out relative rotation relative to fixing component 9b using the power of actuator 17, to make on movable link 9c
Lower movement and the depth for changing recess portion 9a.Furthermore it is also possible to by being set between the inner peripheral surface of cylinder 9 and the peripheral surface of movable link 9c
For screw pair.
Also, control device 19 shown in FIG. 1 controls actuator 17 and sets the upper and lower position of movable link 9c.For example,
Control device 19 controls actuator 17, and the depth of recess portion 9a is made to increase with the rising of the load of diesel engine.
Next, being illustrated to the action of exhaust valve actuator 1 constituted as described above.
When the rotation of the cam 35 (camshaft 43) of hydraulic pressure supplying device 13, the cam of 41 1 edge cam 35 of cam roller
Profile rotates, and moves up and down on one side, and jumper bar 31 should be made to be slided up and down in cylinder 33 up and down through connecting shaft 39.
When jumper bar 31 slides upward in cylinder 33, the start oil being filled in compression chamber 37 is pressurizeed, the work
Dynamic oil is via oil hydraulic circuit 11 by force feed to the hydraulic chamber 21 between cylinder 9 and piston 7.The volume of hydraulic chamber 21 is because of the start
Oil oil pressure and expand, piston 7 overcomes the force of air spring assembly 15 and is depressed, open air bleeding valve 5.Air bleeding valve 5 is opened
Height of the valve amount by cam 35 apart from basic circle 35a determines.
Also, when cam 35 rotates downwards, jumper bar 31 pushes back lower section by force application mechanism not shown in the figure, is applied to
Oil pressure in compression chamber 37 and hydraulic chamber 21 drops to the weaker benchmark oil pressure supplied from low pressure start oil supply circuit 45.Cause
This, air bleeding valve 5 is elected and closed by the force of air spring assembly 15, and thus piston 7 rises, the volume of hydraulic chamber 21 becomes
The start oil of minimum, hydraulic chamber 21 backflows via oil hydraulic circuit 11 to the compression chamber 37 of cylinder 33.
So, hydraulic pressure supplying device 13 is driven by cam 35 and at the defined valve opening moment intermittently to cylinder 9
For oil feed pressure, pushing piston 7 makes air bleeding valve 5 open.
Also, when by jumper bar 31, under pressure, a small amount of start oil in hydraulic chamber 21 is from the throttling section in circuit 25
Stream device 27 is discharged to the outside of oil hydraulic circuit 11.As a result, backflowing from hydraulic chamber 21 to compression chamber in 5 valve closing of air bleeding valve
37 oil mass is less than the oil mass for being delivered to hydraulic chamber 21 from compression chamber 37 under pressure by jumper bar 31, and piston 7 can be made proper
The topmost of cylinder 9 is risen to well and closes air bleeding valve 5 conscientiously.When jumper bar 31 is not pushed by cam 35, from throttling set 27
The start oil of the deal of discharge is replenished to oil hydraulic circuit 11 from low pressure start oil supply circuit 45.
Fig. 4 is the lifting amount of the lifting amount (a) for indicating cam 35, the start oil pressure (b) in hydraulic chamber 21 and air bleeding valve 5
(c) chart of relationship.In Fig. 4 (b), (c), the depth h that line indicated by the solid line is recess portion 9a shown in Fig. 2 (a) is zero
When start oil pressure and air bleeding valve lifting amount.
At the t0 moment, when cam lifting amount increases with the profile of cam 35 and jumper bar 31 starts to be promoted, hydraulic chamber
21 start oil pressure is begun to ramp up from reference pressure.At the t1 moment, cam lifting amount reaches maximum value, and jumper bar 31 is raised supreme
Dead point, start oil pressure reach maximum value, at this time at the t2 moment, the force of the oil pressure counter air spring assembly 15 of hydraulic chamber 21 and
Cylinder pressure and piston 7 is forced down.
The lifting amount of air bleeding valve 5 increases as a result, in 5 standard-sized sheet of t3 moment air bleeding valve.At this moment, the volume of hydraulic chamber 21 with
It forces down piston 7 and expands, thus while the oil pressure in hydraulic chamber 21 strongly reduces, but can also be maintained open needed for air bleeding valve 5
Oil pressure.Therefore, during jumper bar 31 maintains top dead-centre with the profile of cam 35, the lifting amount of air bleeding valve 5 is also tieed up
It holds in maximum, air bleeding valve 5 is maintained at valve opening state.
At the t5 moment, when cam lifting amount reduces with the profile of cam 35 and jumper bar 31 is begun to decline, hydraulic chamber
21 start oil pressure also begins to decline.When start oil pressure drops to specified value, the force and cylinder internal pressure of air spring assembly 15
Power is got the upper hand, and piston 7 is pushed to top since the t6 moment, and thus the lifting amount of air bleeding valve 5 starts to reduce.When the liter of cam 35
When drop amount is zero and jumper bar 31 drops to bottom dead centre, air bleeding valve 5 completely closes at the t7 moment.Also, the start of oil hydraulic circuit 11
Oil pressure restores to reference pressure.
As shown in Fig. 2 (a), when movable link 9c relative to the fixing component 9b of cylinder 9 declines and formed the recess portion of depth h
When 9a, if air bleeding valve 5 is closed, the piston 7 integrally acted with air bleeding valve 5 enters the inside of cylinder 9, thus hydraulic chamber 21
Volume reduces, and the start oil being filled in hydraulic chamber 21 is released from oil hydraulic circuit 11 and backflowed to compression chamber 37.
At this moment, since the start oil in hydraulic chamber 21 can successfully flow into oil hydraulic circuit 11 until the protrusion 7a of piston 7 is inserted
Enter the recess portion 9a of cylinder 9, therefore piston 7 enters the inside of cylinder 9,5 quick closedown of air bleeding valve with faster speed.Then, such as
Shown in Fig. 2 (b), when protrusion, 7a is initially inserted into recess portion 9a, hydraulic chamber 21, which is divided into, to be formed in around the 7a of protrusion
The room 21a and room 21b being formed in inside recess portion 9a.
Start oil in the 21b of room is smoothly discharged from oil hydraulic circuit 11 as former state, and the start oil in enclosed room 21a then passes through
Narrow gap between room 21a and room 21b flows into room 21b and then is discharged by oil hydraulic circuit 11.Therefore, with start
Huge flow resistance when oil passes through gap generates cushioning effect (Cushioning Action) to the action of piston 7, reduces
The valve closing speed of air bleeding valve 5, at the time of having delayed until air bleeding valve 5 completely closes.
If the depth h of recess portion 9a is smaller, the required oil mass due to flowing into room 21b from room 21a is reduced, in piston 7
Ascending motion in apply cushioning effect time shorten.Therefore, air bleeding valve 5 will be in the close profile defined by cam 35
The more early moment at valve closing moment closes.
Also, increasing with the depth h of recess portion 9a, the required oil mass due to flowing into room 21b from room 21a increases,
It is more time-consuming when discharge, and in the ascending motion of piston 7 apply cushioning effect time lengthening.Therefore, air bleeding valve 5 will than by
The valve closing moment of the profile defined of cam 35 closes at the time of significantly delaying.
So, it will be terminated in the uphill process of piston 7, the protrusion 7a of piston 7 is inserted into the recess portion 9a of cylinder 9
When, the start oil due to enclosing room 21b will produce flow resistance, in the pressure such as Fig. 4 (b) in hydraulic chamber 21 (room 21a)
Dotted line P1, P2 shown in steeply rise.Dotted line P1 indicates that the pressure rate of rise when depth h of recess portion 9a is smaller, dotted line P2 indicate
Pressure rate of rise when the depth h of recess portion 9a is larger.
So, since pressure P1, P2 in hydraulic chamber 21 drastically increases, such as dotted line L1, L2 in Fig. 4 (c)
Shown, when air bleeding valve 5 will close, the slip of lifting amount occurs slowly to tilt.The reduction of the lifting amount of air bleeding valve 5
Pressure of the rate in hydraulic chamber 21 is part shown in dotted line L1 when being P1, and the pressure in hydraulic chamber 21 is dotted line L2 when being P2
Shown in part.That is, the depth h of recess portion 9a is bigger, until air bleeding valve 5 completely closes the required time, longer (the valve closing moment gets over
It delays).Therefore, air bleeding valve 5 will contact valve seating (valve seat) with more slow speed, caused by the collision with valve seating
Impact.
So, by changing the depth being arranged in the recess portion 9a of 9 side of cylinder, the close moment of air bleeding valve 5 can be made
It approaches or is later than by the valve closing moment of the cam contour defined of cam 35, therefore the characteristic adaptation of diesel engine can be made to operate shape
Condition.
Also, the change of 5 close moment of air bleeding valve be due to that can use the depth of recess portion 9a for changing and being arranged on cylinder 9,
Movable link 9c is set to relatively move such simple knot in the axial direction relative to the fixing component 9b of cylinder 9 using actuator 17
Structure is completed, therefore can be as the structure of the marine diesel suitable for being desirable for simple structure.
In addition, control device 19 controls actuator 17, the depth h of recess portion 9a is made to increase with the increase of the load of diesel engine
Greatly.Therefore, with the raising of the load of diesel engine, the close moment of air bleeding valve 5 is delayed.Thereby, it is possible to prevent high loaded process
When cylinder in gas compression pressure it is excessively high and improve the durability of diesel engine.
Fig. 3 (a), (b) are the longitudinal sections of the other shapes example of the recess portion 9a of the protrusion 7a and cylinder 9 that indicate piston 7.
Here, the protrusion 7a being arranged on the top surface of piston 7 is with prominent for cylindric side around the top surface of piston 7
Formula is formed.In addition, the recess portion 9a being arranged in the inside top surface of cylinder 9 is formed in the week of inside top surface as the recess of tubular
It encloses.That is, the radially inner and outer position relationship of protrusion 7a shown in Fig. 2 (a), (b) and recess portion 9a is reversed.
The depth h of recess portion 9a can change between from zero to height identical with the height of protrusion 7a.Example
Such as, being arranged can move up and down in the columned movable link 9d of the top center of cylinder 9, when movable link 9d is from cylinder
When 9 inside top surface protrudes, recess portion 9a is formed between the inner peripheral surface and the peripheral surface of movable link 9d of cylinder 9.
The outer diameter of movable link 9d is set as when piston 7 rises, and the protrusion 7a of piston 7 is separated with several millimeters or so of gap
Size around movable link 9d.Movable link 9d is driven upside down by actuator 17 shown in FIG. 1, thus changes recess portion
The depth h of 9a.Also, oil hydraulic circuit 11 is open to the lower surface of movable link 9d.
As shown in Fig. 3 (a), when forming the recess portion 9a of depth h when the movable link 9d declines of cylinder 9, if air bleeding valve 5 closes
It closes, then the piston 7 integrally acted with air bleeding valve 5 enters the inside of cylinder 9, and thus the volume of hydraulic chamber 21 reduces, and is filled in
Start oil in hydraulic chamber 21 is released from oil hydraulic circuit 11 and is backflowed to compression chamber 37.
At this moment, since the start oil in hydraulic chamber 21 can successfully flow into oil hydraulic circuit 11 until the protrusion 7a of piston 7 is inserted
Enter the recess portion 9a of cylinder 9, therefore piston 7 enters the inside of cylinder 9,5 quick closedown of air bleeding valve with faster speed.Then, such as
Shown in Fig. 3 (b), when protrusion, 7a is initially inserted into recess portion 9a, hydraulic chamber 21 is divided into the inner circumferential side for being formed in protrusion 7a
Room 21a and the room 21b that is formed in inside recess portion 9a.
Start oil in the 21a of room is smoothly discharged from oil hydraulic circuit 11 as former state, and the start oil in enclosed room 21b then passes through
Narrow gap between room 21b and room 21a flows into room 21a and then is discharged by oil hydraulic circuit 11.Therefore, with start
Huge flow resistance when oil passes through gap generates cushioning effect (Cushioning Action) to the action of piston 7, reduces
The valve closing speed of air bleeding valve 5, at the time of having delayed until air bleeding valve 5 completely closes.Air bleeding valve can either be protected as a result,
5 from the impact caused by the collision with valve seating, and can make the characteristic adaptation operational situation of diesel engine.
The case where with the structure in Fig. 2 (a), (b), is identical, and the depth h of recess portion 9a is bigger, the flow resistance institute of start oil
The time that the cushioning effect (Cushioning Action) of generation is acted on is longer.That is, the depth h of recess portion 9a can be made bigger,
The valve closing moment of air bleeding valve 5 is more delayed.
According to the structure of the Fig. 3 (a), (b), can make to tie shown in structure ratio Fig. 2 (a) of the height of change recess portion 9a, (b)
Structure is simpler.
[the 2nd embodiment]
Fig. 5 is the summary composition figure for indicating the exhaust valve actuator involved by second embodiment of the present invention.In the exhaust
In valve drive 51, with the exhaust valve actuator 1 of the 1st embodiment the difference is that, without the top surface of piston 7
The recess portion of the inside top surface of protrusion and cylinder 9；Leakage path 53 is branched out from the branch point 11d of oil hydraulic circuit 11, and wherein
Way connection can change the variable throttling device thereof (flow control device) 55 of the area of passage of leakage path 53.Due to other parts
Structure and effect it is identical as the exhaust valve actuator 1 of the 1st embodiment, therefore various pieces are marked into identical label
And omit respective description.
The amount of restriction of variable throttling device thereof 55 is controlled by control device (control mechanism) 57.Control device 57 controls
The amount of restriction of variable throttling device thereof 55 makes the area of passage of leakage path 53 reduce with the rising of the load of diesel engine.Separately
Outside, flow control valve etc. can be set and replace variable throttling device thereof 55.
It is identical as the exhaust valve actuator 1 of the 1st embodiment according to the exhaust valve actuator 51, when oil pressure supplies
When device 13 is driven by cam 35, at the defined valve opening moment to cylinder 9 for oil feed pressure, the piston 7 inside cylinder 9 is thus pushed
And open air bleeding valve 5.Also, when interrupt to cylinder 9 for oil feed pressure when, air bleeding valve 5 due to air spring assembly 15 force and
It closes.
A part for the start oily (oil pressure) supplied from hydraulic pressure supplying device 13 is variable from what is be arranged on leakage path 53
Throttling set 55 leaks into the outside of oil hydraulic circuit 11.It backflows as a result, from cylinder 9 to hydraulic pressure supplying device when 5 valve closing of air bleeding valve
13 oil mass be less than by hydraulic pressure supplying device 13 under pressure force feed to cylinder 9 oil mass.Therefore, it is possible in air bleeding valve 5
Just so that piston 7 is risen to the topmost in cylinder 9 when valve closing, and air bleeding valve 5 can be closed conscientiously.
By controlling variable throttling device thereof 55, the start oil supplied from hydraulic pressure supplying device 13 can be adjusted and leak into outside
Amount.When the leakage rate is smaller, the speed that air bleeding valve 5 is closed slows down, when leakage rate is larger, the speed of the closing of air bleeding valve 5
Accelerate.
So, by the way that variable throttling device thereof 55 is arranged on leakage path 53, it can shift to an earlier date or delay air bleeding valve 5
Close moment, therefore the characteristic adaptation operational situation of diesel engine can be made, wherein the leakage path 53 is from hydraulic pressure supplying device
11 top set of oil hydraulic circuit between 13 and cylinder 9 and go out.
Also, the change of 5 close moment of air bleeding valve in oil hydraulic circuit 11 due to can be with being arranged leakage path 53 and can
Simple structure as variable throttling device 55 is completed, therefore the marine diesel suitable for being desirable for simple structure.In addition,
Leakage path 53 not necessarily goes out from 11 top set of oil hydraulic circuit, can also from such as cylinder 9 branch and go out.
Fig. 6 is the lifting amount (a) for indicating the cam 35 on exhaust valve actuator 51, the start oil pressure in hydraulic chamber 21
(b) and the chart of the relationship of the lifting amount (c) of air bleeding valve 5.Due to elemental motion and the 1st embodiment illustrated in fig. 4
The case where exhaust valve actuator 1, is identical, therefore omits repeated explanation.
When the amount of restriction of the variable throttling device thereof 55 of leakage path 53 is minimum, and air bleeding valve 5 is valve closing, due to hydraulic chamber
Start oil in 21 backflows to hydraulic pressure supplying device 13 and can't reveal very much, therefore rising will more in cylinder 9 for piston 7
It takes.Therefore, as shown in solid in Fig. 6 (b), the decline situation of the start oil pressure in hydraulic chamber 21 and the lifting amount of cam 35
Decrement be consistent.Also, the reduction situation of the lifting amount of air bleeding valve 5 such as shown in solid in Fig. 6 (c), the closing of air bleeding valve 5
Moment is delayed.
In addition, when the amount of restriction of variable throttling device thereof 55 expands, since the leakage rate of the start oil in hydraulic chamber 21 increases
It is more, therefore the amount backflowed to the start oil of hydraulic pressure supplying device 13 out of hydraulic chamber 21 will be reduced, piston 7 is upper in cylinder 9
Rising the time will shorten.Therefore, as shown in the dotted line in Fig. 6 (b), the decline situation of the start oil pressure in hydraulic chamber 21 is than cam 35
The decrement of lifting amount reduce faster.Also, the reduction situation of the lifting amount of air bleeding valve 5 such as the dotted line institute in Fig. 6 (c)
Show, the close moment of air bleeding valve 5 shifts to an earlier date.
As described above, control device 57 controls the amount of restriction of variable throttling device thereof 55, make the area of passage of leakage path 53
Reduce with the rising of the load of diesel engine.Therefore, as the load of diesel engine rises, the close moment of air bleeding valve 5 is delayed,
It can prevent when high loaded process that the compression pressure of gas in cylinder is excessively high and improves the durability of diesel engine.
In addition, as improvement, as shown in broken line in fig. 5, it can be arranged and be connected to hydraulic chamber 21 and oil hydraulic circuit 11
Between leakage path 53a, and on leakage path 53a be arranged variable throttling device thereof 55a, so as to adjust air bleeding valve 5
The rise time of piston 7 when valve closing.
Shown in as described above, exhaust valve actuator 1,51 involved according to the embodiment of the present invention and have
The diesel engine of the exhaust valve actuator can utilize the simple structure suitable for marine diesel, change the closing of air bleeding valve 5
At the moment, make the characteristic adaptation operational situation of diesel engine, and the reliability and durability of internal combustion engine can be improved, additionally aids simultaneously
Save fuel etc..
In addition, the present invention is not limited to the composition of the above embodiment, in the range for the purport for not departing from the present invention
Interior suitably to change or improve, the embodiment after so changing or improveing is also contained in the right of the present invention
In range.
Symbol description
1,51 exhaust valve actuator
5 air bleeding valves
7 pistons
The protrusions 7a
9 cylinders
9a recess portions
11 oil hydraulic circuits
13 hydraulic pressure supplying devices (oil pressure feed mechanism)
15 air spring assemblies (valve closing force application mechanism)
17 actuators
19,57 control devices (control mechanism) and
21 hydraulic chamber
31 jumper bars
35 cams
37 compression chambers
53 leakage paths
55 variable throttling device thereofs (flow control device)
Claims (6)
1. a kind of exhaust valve actuator, which is characterized in that have：Piston is arranged on the air bleeding valve of internal combustion engine；Cylinder,
It accommodates the piston；Oil pressure feed mechanism is connect via oil hydraulic circuit with the cylinder, by actuated by cams and defined
The valve opening moment, and pushing the piston made the air bleeding valve open intermittently to the cylinder for oil feed pressure；Valve closing force machine
Structure exerts a force to the air bleeding valve to valve closing direction；Protrusion is formed on the top surface of the piston and with than the piston
The small topside area of cross-sectional area；Recess portion is formed in the inside top surface of the cylinder, when the piston rises, institute
It states protrusion and is separated with and be inserted into gap in the recess portion；Actuator changes the depth of the recess portion；And control mechanism,
The actuator is controlled,
The cylinder has：Positioned at the columned first component of central part；And be arranged around the first component and
Relative to the second component of the relatively-movable cylindrical shape of the first component,
The lower surface of the first component is located at the top of the lower surface of the second component, and the recess portion is the first component
Lower section, the space of the inner circumferential side of the second component,
The actuator changes the depth of the recess portion by the movement second component.
2. a kind of exhaust valve actuator, which is characterized in that have：Piston is arranged on the air bleeding valve of internal combustion engine；Cylinder,
It accommodates the piston；Oil pressure feed mechanism is connect via oil hydraulic circuit with the cylinder, by actuated by cams and defined
The valve opening moment, and pushing the piston made the air bleeding valve open intermittently to the cylinder for oil feed pressure；Valve closing force machine
Structure exerts a force to the air bleeding valve to valve closing direction；Protrusion is formed on the top surface of the piston and with than the piston
The small topside area of cross-sectional area；Recess portion is formed in the inside top surface of the cylinder, when the piston rises, institute
It states protrusion and is separated with and be inserted into gap in the recess portion；Actuator changes the depth of the recess portion；And control mechanism,
The actuator is controlled,
The cylinder has：Positioned at the columned third component of central part,
The lower surface of the third component is located at the lower section of the inside top surface of the cylinder, and the recess portion is the inner circumferential of the cylinder
Space between face and the peripheral surface of the third component,
The actuator changes the depth of the recess portion by the movement third component.
3. exhaust valve actuator according to claim 1 or 2, which is characterized in that held described in the control mechanism control
Row device makes the depth of the recess portion increase with the rising of the load of the internal combustion engine.
4. a kind of exhaust valve actuator, which is characterized in that have：Piston is arranged on the air bleeding valve of internal combustion engine；Cylinder,
It accommodates the piston；Oil pressure feed mechanism is connect via oil hydraulic circuit with the cylinder, by actuated by cams and defined
The valve opening moment, and pushing the piston made the air bleeding valve open intermittently to the cylinder for oil feed pressure；Valve closing force machine
Structure exerts a force to the air bleeding valve to valve closing direction；Leakage path, from the connection oil pressure feed mechanism and the cylinder
Branch in the oil hydraulic circuit and go out；Flow control device changes the area of passage of the leakage path；And control machine
Structure controls the flow control device, wherein the control mechanism controls the flow control device, makes the air bleeding valve
The oil mass backflowed from the cylinder to the oil pressure feed mechanism when valve closing is less than through the oil pressure feed mechanism for oil feed pressure
When supply to the oil mass of the cylinder.
5. exhaust valve actuator according to claim 4, which is characterized in that the control mechanism controls the flow tune
Mechanism is saved, the area of passage of the leakage path is made to reduce with the rising of the load of the internal combustion engine.
6. a kind of internal combustion engine, which is characterized in that with the exhaust valve actuator described in any one of claim 1,2,4 or 5.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013267798A JP6092090B2 (en) | 2013-12-25 | 2013-12-25 | Exhaust valve driving device and internal combustion engine provided with the same |
| JP2013-267798 | 2013-12-25 | ||
| PCT/JP2014/075754 WO2015098219A1 (en) | 2013-12-25 | 2014-09-26 | Exhaust valve drive device and internal combustion engine equipped with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105814290A CN105814290A (en) | 2016-07-27 |
| CN105814290B true CN105814290B (en) | 2018-11-02 |
Family
ID=53478099
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480062833.9A Expired - Fee Related CN105814290B (en) | 2013-12-25 | 2014-09-26 | Exhaust valve actuator and internal combustion engine with the exhaust valve actuator |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6092090B2 (en) |
| KR (2) | KR20160147070A (en) |
| CN (1) | CN105814290B (en) |
| WO (1) | WO2015098219A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6034922B1 (en) | 2015-06-22 | 2016-11-30 | 富士重工業株式会社 | Vehicle control device |
| CN106703928B (en) * | 2016-12-28 | 2022-07-15 | 沪东重机有限公司 | Exhaust valve control execution system directly driven by servo oil |
| CN108868936B (en) * | 2018-06-13 | 2020-09-08 | 中国北方发动机研究所(天津) | High-compactness hydraulic tappet of internal combustion engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1033091A (en) * | 1987-11-05 | 1989-05-24 | 奥格斯堡·纽伦堡机械公司伯迈斯特与韦恩柴油机分公司 | Control the method for the closing movement of the outlet valve that surges of marine diesel engine and be used for the outlet valve of the method |
| CN103277163A (en) * | 2013-05-07 | 2013-09-04 | 江苏公大动力技术有限公司 | Variable-lift driver |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0158740U (en) * | 1987-10-06 | 1989-04-12 | ||
| JPH0726922A (en) * | 1993-07-07 | 1995-01-27 | Zexel Corp | Valve control device for internal combustion engine |
| JPH094425A (en) * | 1995-06-19 | 1997-01-07 | Nissan Motor Co Ltd | Variable valve gear for internal combustion engine |
| JP3160502B2 (en) * | 1995-09-01 | 2001-04-25 | 日鍛バルブ株式会社 | Hydraulic intake and exhaust valve drive with damper |
| JP2964235B2 (en) | 1998-03-04 | 1999-10-18 | 株式会社グリーンライフ | Planter suspension |
| JP4043136B2 (en) * | 1999-03-30 | 2008-02-06 | 三菱重工業株式会社 | Hydraulic exhaust valve drive device |
-
2013
- 2013-12-25 JP JP2013267798A patent/JP6092090B2/en active Active
-
2014
- 2014-09-26 CN CN201480062833.9A patent/CN105814290B/en not_active Expired - Fee Related
- 2014-09-26 KR KR1020167035103A patent/KR20160147070A/en active Search and Examination
- 2014-09-26 KR KR1020167011745A patent/KR101727872B1/en active IP Right Grant
- 2014-09-26 WO PCT/JP2014/075754 patent/WO2015098219A1/en active Application Filing
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1033091A (en) * | 1987-11-05 | 1989-05-24 | 奥格斯堡·纽伦堡机械公司伯迈斯特与韦恩柴油机分公司 | Control the method for the closing movement of the outlet valve that surges of marine diesel engine and be used for the outlet valve of the method |
| CN103277163A (en) * | 2013-05-07 | 2013-09-04 | 江苏公大动力技术有限公司 | Variable-lift driver |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2015098219A1 (en) | 2015-07-02 |
| KR101727872B1 (en) | 2017-04-17 |
| JP2015124631A (en) | 2015-07-06 |
| KR20160147070A (en) | 2016-12-21 |
| JP6092090B2 (en) | 2017-03-08 |
| CN105814290A (en) | 2016-07-27 |
| KR20160067918A (en) | 2016-06-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101019859B1 (en) | Lost motion system and method for fixed-time valve actuation | |
| KR100820694B1 (en) | Variable valve lift apparatus | |
| CN101743384B (en) | Variabale valve actuation system | |
| JP4383875B2 (en) | Method and system for improving engine braking by variable valve drive | |
| CN101994536B (en) | Intake valve closing hydraulic adjuster | |
| CN102105657B (en) | Control arrangement in piston engine | |
| KR101244845B1 (en) | Variable valve lift apparatus for engine | |
| JP2005256843A (en) | Cross-head type large two-stroke type diesel engine | |
| CN101627195A (en) | Engine brake apparatus | |
| CN105814290B (en) | Exhaust valve actuator and internal combustion engine with the exhaust valve actuator | |
| US8646422B2 (en) | Electro-hydraulic variable valve lift apparatus | |
| KR101092806B1 (en) | Continuously variable valve lift device of vehicle | |
| JP2012219708A (en) | Variable compression ratio engine | |
| KR101623222B1 (en) | Variable valve timing system using hydraulic system | |
| CN205089460U (en) | Compression release type engine brake device | |
| US7673602B2 (en) | Variable valve mechanism | |
| KR101305200B1 (en) | Electro-hydraulic variable vavlve lift system | |
| CN105705738A (en) | Exhaust-valve drive device and internal combustion engine provided with same | |
| KR101234653B1 (en) | Varible vavle lift apparatus | |
| CN113574250B (en) | Valve actuating mechanism and engine | |
| CN207093167U (en) | A kind of slow seating arrangement for slowing down valve crash speed | |
| WO1997019260A1 (en) | Valve operating system | |
| JP2009041520A (en) | Engine | |
| KR20090051489A (en) | Valve tappet for cylinder de-activation device of vehicle | |
| AU714090B2 (en) | Valve operating system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20170814 Address after: Japan's Tokyo port harbor two chome 16 No. 5 Applicant after: MITSUBISHI HEAVY INDUSTRIES, Ltd. Applicant after: JAPAN ENGINE Corp. Address before: Japan's Tokyo port harbor two chome 16 No. 5 Applicant before: MITSUBISHI HEAVY INDUSTRIES, Ltd. |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20181102 |